Hydraulic driving mechanism



Nov. 21, 1961 J. L. MENNITT ET AL HYDRAULIC DRIVING MECHANISM 6 Sheets-Sheet 1 Filed April 16, 1959 8 MT 4 F N WW w E T M ,um A A 1 4 W a 0 J5 Nov. 21, 1961 J. 1.. MENNlTT ET AL 3,009,444

HYDRAULIC DRIVING MECHANISM Filed April 16, 1959 6 Sheets-Sheet 2 3/ INVENTOR.

ATTOIQNEYS Nov. 21, 1961 MENNITT AL 3,009,444

HYDRAULIC DRIVING MECHANISM Filed April 16, 1959 6 Sheets-Sheet 3 0 w' A TTORNEYS Nov. 21, 1961 J. 1.. MENNlTT ET AL HYDRAULIC DRIVING MECHANISM Filed April 16, 1959 l NVEN TOR. JaJaPx/ A ME EVJ'TA E ATTORNEYS Nov. 21, 1961 J. MENNITT ETAL 3,009,444

HYDRAULIC DRIVING MECHANISM Filed April 16, 1959 6 Sheets-Sheet 5 1' V /3z I84 32 I I Q '224 TTORNEYQY Nov. 21, 1961 J. MENNITT ETAL 3,009,444

HYDRAULIC DRIVING MECHANISM Filed April 16, 1959 m 6 Sheets-Sheet 6 ATTORNE Y5 3,009,444 Patented Nov. 21, 1961 3,009,444 HYDRAULIC DRIVING MECHANISM Joseph L. Mennitt, Toledo, Ohio, and Eustace H. Munford, Ottawa Lake, Mich, assignors to Owens-Illinois Glass Company, a corporation of Ohio Filed Apr. 16, 1959, Ser. No. $436,957 14 Claims. (Cl. 121-38) This present invention is directed to an improvement in hydraulic driving devices and is particularly directed to a device designed to he used as a power element in the production of driving power for tables, conveyors or other movable apparatus which is to be driven intermittently and in a single direction of movement.

As one illustration of the application of this invention it is herein illustrated and described as applied for driving a unit of a glass forming machine, and in particular for driving the mold carrying table of such a machine wherein molding units are to be successively presented to a plurality of forming stations in intermittent succession.

The primary object of this invention is to provide a hydraulic motor adapted to drive or index a transporting element in a single direction but with the application of the driving power being intermittently applied.

A further object is the provision of such a drive mechanism wherein the rate of the rotary movement may be readily controllable during indexing.

A still further object is the provision of a mechanism wherein the rest or idle position of the driven element or mold table may be brought into accurate register at each successive position.

Further objects will be apparent from the drawings and the following descriptive matter as hereinafter set forth.

The invention is illustrated in the accompanying drawings in which:

FIG. 1 is a side elevation of a glass forming machine to which this present invention is readily applicable;

FIG. 2 is a plan view, in part-section, illustrating the arrangement of the cushioning control cams for the table indexing and their valve mechanisms;

FIG. 3 is a sectional elevation, taken at line 3-3 on FIG. 2 illustrating the general organization of the mechanisms of this driving device;

FIG. 4 is a sectional plan view taken at line 4 4 on FIG. 3 illustrating the lluid passages leading to the rotary members;

FIG. 5 is a sectional plan view taken at line 5-5 on FIG. 3 and illustrates the locking device for the motor drive case;

FIG. 6 is a part-sectional plan view taken at line 6-6 on FIG. 3 illustrating the slip motion connection between the control cams and the drive shaft;

FIG. 7 is a plan view in section taken at line 7-7 on FIG. 3 and illustrates the relative position of rotor and casing vanes at the completion of the index movement of the rotor casing;

FIG. 8 is a further sectional view taken at line 7-7 on FIG. 3 illustrating the relative position of the rotor and casing at the completion of the index motion of the rotor shaft;

FIG. 9 is also a sectional plan view taken at line 9-9 on FIG. 3 illustrating the casing stop member which is formed as part of the rotor shaft and also illustrating the relative position of this member and the other parts of the mechanism when the parts are in the position shown in FIG. 7;

FIG. 16 is also a sectional plan view taken at line 9-9 on FIG. 3 showing the relationship of the several mechanical parts when the parts are in position shown in FIG. 8;

FIG. 11 is a sectional elevational view taken at line 11-11 on FIG. 5, of a portion of the fluid pressure circuit;

FIG. 12 is a further vertical section taken at line 12-12 on FIG. 5 illustrating other portions of the fluid pressure circuit to the motor drive;

FIG. 13 is a fragmentary part in sectional plan view taken at line 13-13 on FIG. 3 showing the valve by which the flow of fluid pressure is feathered or controlled;

FIG. 14 is a diagrammatic view of the fluid pressure circuit for the rotor actuation; and

FIG. 15 is a flow control diagram for the control of the turret locking and unlocking mechanism.

The hydraulic motor proper, as it is specifically illustrated in FIGS. 2, 3, 4, 5 and 7-10 comprises a rotor casing 1% having an inner chamber 11 containing a rotatably supported rotor sleeve 12 which in turn carries a pair of oppositely disposed impellers or vanes 14 and 14- arranged to provide a means of rotary movement to the rotor sleeve 12 within the chamber 11 and relative to the casing Ill. Mounted on the inner surface of the side wall of chamber 11 is a further pair of oppositely disposed impellers or vanes 15 and 15 which are arranged to drive or rotate the casing 10 with respect to the rotor sleeve 12. The rotor sleeve 12 is keyed as at 18 to a vertical shaft 18 mounted in bearing 244 inserted in a support 21. The support 21 is mounted upon the main machine frame 22 and carries a bracket 20.

Attached to the lower end of shaft 18 is a mold carrying turret 26 upon which is mounted a plurality of neck mold units 25. These units 25 are so arranged on said carrier turret as to be positioned successively at the ware forming and takeout stations (A and B respectively) with each index of the turret 26.

Positioned intermediate the rotary oil connection 19 and bracket 2G is a valve block Sil which is attached to the bracket 20 by screws 31 and to the rotary oil connection 19 by slot 196 (see FIG. 4). A cap 32 provides a structure for supplying pressure fluid to this valve block 30. The valve block 30 carries a pair of snubbing valves 181 and 216 which are controlled by cams 180 and 218 respectively (FIGS. 3 and 14), and adapted to control the rate or speed of the rotary movement of both the rotor case 10 and the rotor shaft 18. In addition, the valve block 30 also carries a locking apparatus for the casing 16 and a time delay valve 203 which permits the case locking detent 125 to seat in locking position in notch 126 prior to the application of pressure to the rotor impellers or vanes 14 and 14a of the rotor sleeve 12'.

By reference to FIG. 2, it will 'be noted that the control cam 180, for controlling the movement of the rotor shaft 18, is shown with the snubber valve roller 181 on the low portion 186, thus leaving the tapered portion 217 of valve 181 in open position. Leaving this valve in open position is accomplished through a lost motion arrangement which is obtained through engagement provided by a pin 35, mounted in the cam 218, and arranged for movement in the slot 36 formed in the under face of the cam Slot 36 has a length of less than 120. An expansion spring 38 and a link pin 39 are mounted in the opening 40 of the spacer plate 41 and normally retain the cam 180 and the spacer plate 41 in a position op posite to that shown in FIG. 2. The spacer plate 41 is keyed to shaft 13 as at 43 (FIG. 3).

Cam 218 is indexed by being moved along with the rotor case 10, and the pin 35 will during this period slide counterclockwise in groove 36 until it reaches the end of this groove, where it will pick up the cam 180 and move it also counterclockwise, thus compressing the springs 38 to an amount equal to the length of slots 45. Bolts 46 are provided to retain cam 180, not limit its rotation. Rotary motion of cam 180 is controlled by the difference between 120 and the length of slot 36 (in this instance 15), thus placing the low portion 180 of the cam 180 as shown in FIG. 2, that is, with the snubber valve 181 in an open position. The locking detent 125 will then look the casing 10 against further movement. The cams 130 and 218, the rotor casing 10 and rotor sleeve 12 are shown in FIGS. 2, 7 and 9 in the position where the rotor sleeve 12, shaft 18 and table 26 are ready to be indexed under control of the main cam 110 on cam drum 112.

Subsequently, the casing 10 will be indexed, also counter-clockwise, and then next the table 26 will be indexed.

To initiate this operation, the timer cam 110 will shift valve 100 and withdraw the locking detent 125 from its slot 126.

Starting with motor parts as shown in FIG. 2, the turret 26 is ready for indexing. For the first of turret rotation, the cam 130 is held stationary by springs 38. After the first 15 of rotation, the bolt 46 reaches the end of slot 45 and starts to move cam 180 so that it is now rotating with the turret 26. Valve 181 remains open until cam 180 permits it to close at or during the end of the turret index, thus snubbing the turret movement as it comes into the station. At this time the valve 181 is closed tight and must be opened before another turret index can take place. This opening is accomplished when pin moves cam 180 ahead 15 at the end of the indexing of case 10.

With the completion of the formation of a parison at station #1 and a blown bottle at station #2, the table or turret 26 will be ready to be indexed under control of the valve 100 and the cam 110 formed as a part of the main cam drum 1-12 mounted in the main frame 21 of the forming machine.

The main cam drum 112 may be driven through a driven gear 88 by a pinion 89 on a drive shaft 90. Drive shaft 90 will be driven by any one of several well known variable speed motor drives (not shown).

The drive for the indexing of the turret 26 is a fluid drive type and as shown in FIG. 14, the turret 26 has just completed its indexing movement, the driving parts are at rest, and the locking detent 114 has moved into the locking position in the turret 26, as shown in FIGS. 1 and 15, thus maintaining the turret 26 in locked registered relationship with the several forming stations.

The valve 100 is now moved by cam 110, shifting the valve to permit pressure fluid to flow from chamber 116 in the main valve block 117 through recess 123 in valve 100 into the conduits 119 and 120, to chamber 121, formed in the valve support block 30 and beneath the piston 122. This pressure moves the piston 122 into con tact with arm 124 on detent 125 to withdraw the drive case locking detent 125 from the groove 126, thus freeing the drive case 10 for rotation. As the locking detent 125 continues to move, it permits fluid to flow through chamber 130 into conduits 131, 132 and 133. A rotary valve arrangement 135 and 136 formed in the joint 19 permits rotation of the driven parts relative to the source of fluid supply.

As the fluid flows into and through conduit 133, it enters or passes through the rotary valve 135. The pressure fluid may then go directly to conduit 155 and chamber 11 or if a safety measure is desired, it may pass to conduit 140 in the lug portion 142 of the blowhead cylinder 143 (FIG. 14). When the blowing of the bottle is completed and the blowhead 145 is raised by piston 147, under control of valve 115 and cam 116 on the main cam drum 110, a port 150 in the piston rod 151 is brought into alignment with the conduit 40. At this time the parts are in the position shown in FIG. 8 and this permits the fluid presure to enter conduit 154, thence through rotary valve 135 into conduit 155 where it enters into one end of a chamber 11 between the impeller 15 and impeller 14 on the sleeve 12 which is keyed at 18 to the turret shaft 18. Due to the turret 26 being locked by detent 114, this pressure causes the drive case 10 and impellers 15 and 15 to rotate in a counter-clockwise direction until the downwardly extending projection 165 thereof contacts the stop 163 and leaving the parts in the position shown in FIGS. 7 and 9. The Stop 163 is formed by a cut-out portion in a plate 166 and this plate being keyed to the rotor sleeve member 12 as at 16 therefore moves with the turret 26 and turret shaft 18. The relative motion as between case 10 and impeller 14 causes the fluid in chamber 11 to flow or exhaust through conduit 168, rotary valve 136 and line 169 to chamber 171 formed in a valve block 30. The cam 213 will, during this rotation, move with the case 10 and move the valve 216 so that recess 182 will bring the chamber 171 and chamber 185 into communication, in such manner that the rate of exhaust flow of fluid into exhaust line 186 will be controlled and thus control the speed of and cushion the rotary movement of the case 10. The valve will permit the fluid in line 186 to exhaust, through recess 118 into exhaust chamber 215 in valve box 117.

These previously described operations will leave the drive parts in the position shown in FIGS. 7 and 9. The next movement will be the indexing of the turret 26 and to accomplish this, the valve 100 will be placed in the position shown in FIG. 14 by the cam and will allow pressure fluid to flow through recess 118 into conduit 190 and 186, chamber 195 in the valve support 30 and behind the piston 200. This will cause the detent to be moved into recess 126 to lock the case 10 against rotation. The movement of piston 200 opens chamber 202 and allows fluid to flow through conduit 205 in valve bolck 30, forcing the time delay piston 208 into the position shown in FIGS. 3 and 14 and permitting flow of fluid to conduit 169, rotary valve 136, to conduit 16% and into chamber 11. The small end 208- of piston 208 is working against a constant fluid pressure from conduit 222 but its small area permits it to be slowly moved to the open position shown. This delay permits the case 10 to be locked by the detent 125 prior to the entrance of pressure fluid into chamber 11. During this time delay the turret detent 114 (FIGS. 1 and 15) is retracted from the locking position shown in FIGS. 1 and 15, in a manner to be described later, thus freeing the turret 26 for indexing or rotation.

The entry of fluid through conduits 168 and 169 into chamber 11 will cause the impellers 14 and 14 to move, relative to the locked casing 10, thus indexing the turret 26, bringing each neck mold to a succeeding station and moving the stop 163 to the position shown on FIG. 14.

The indexing of the turret 26 together with the movement of impellers 14 and 14 provides a situation wherein the impellers 14 and 14 are moving in chamber 11 with fluid exhausting through conduit and 133. This fluid flows into chamber 210 in valve block 30 and thence through chamber 212 to exhaust through conduits 214 and 119 to the exhaust chamber 215 of the valve block 117 The passage of fluid from chamber 210 to chamber 212 is regulated by a valve stem 181 feathered as at 217 and controlled by a cam 180 on and movable with the turret shaft 18. This regulation permits the rotative speed of the turret 26 to be controlled and cushioned during the indexing thereof.

Constant pressure is supplied through conduits 222, 223 and 224 for the purpose of maintaining the valve stems 216 and 181 in physical contact with the control cams 180 and 218 and to provide the time delay pressure bebind the valve stem 208 of the delay valve 206. From the preceding description it should be apparent that this indexing operation requires that the stop 163 and the turret table 26 be indexed 120, and then followed by the casing 10 and its stop being indexed 120 to catch up with the table 26 and stop 163 This step by step operation occurs in repeated succession with the impellers 14 and 15 following each other in repeated and timed succession. The several cams on cam drum 112 permit the selective operation of these fluid actuated elements in such manner that the turret 26 will always index in the same direction and in proper timed sequence.

Simultaneous with the provision of pressure to line 190, pressure is also provided from valve 400- to conduit 230 (see FIG. 15 connected to a chamber 231 in the support 232 beneath piston 235, thereby shifting the detent 114 from locked to unlocked position out of recess 237 in the turret table 26, freeing same for an indexing movement.

The valve 400, which is of the same structure as valve 100, is under control of cam 41% on the main earn drum and is positioned to permit pressure to flow from chamber 116 through recess 419 in valve 400 to conduit 230 and into the chamber 231 of the valve block 232. This pressure will move piston 235 and 'detent 114 will be released from the lock socket 237 in the turret table 26. This releases the turret 26 and frees shaft 18 for rotation to index the table 26 and to move the neck mold pnits 25 and their shaped pariso-ns to their next operative or blowing station.

With the completion of the index motion of turret 26, the cam 410 will move the valve 409 to the position shown in FIG. 15, thereby placing recess 419, in exhaust position for conduit 23d and recess 418 of valve 400 in a position for pressure from the main pressure chamber 116 to flow through conduit 24 1 behind piston 243 and to move the detent 114 into locking position in the locking slot 237 of the turret 25.

When the blowing station is reached the blow molds 35 close about the pendant parison and the closing movement of the blow molds is simultaneous with the raising of the blank or parison molds at the preceding station for the successive formation of the next parison.

When the turret 26 indexes to the blowing station, presenting a parison for blowing, the neck molds are retained closed around the parison under pressure and are so held against the blowing pressure applied for the parison expansion. Blow-heads 145 are provided at the blowing station for expanding the parison to final form in the blow molds 35.

With the completion of the pressing of a parison at station #1 and the blowing of a bottle at station #2, the turret 26 is again indexed to bring the next newly formed parison from station #1 to the blowing station #2 and the previously blown bottle at station #2 is moved to the take-out station #3.

Upon the neck molds reaching the take-out station #3, a cam on the main oam drum 112 FIG. 1) trips a valve (not shown) to actuate the head 157 and move the rollers 158 and 159 downwardly into the same horizontal plane with formed in the upper surfaces of the neck mold holders 25. The actuation of the head 157 causes the shaft 26% and the rollers 158 and 159 to rotate about the vertical axis of the shaft 266, bringing the rollers into contact with the cam surfaces on the neck molds 25. This contact spreads the neck mold holders 25 and their neck forming halves horizontally apart, thereby releasing the blown ware to a dead plate v161 (FIG. 1) which in turn moves the were to a lower position for discharge from the machine. The details of the neck molds and mechanism for affecting their opening forms no part of this invention and is completely disclosed in copending application Serial No. 774,775, filed November 18, 1958, and assigned to the assignee of this application. With the release of the ware from the neck molds, the turret 26 is then indexed and the foregoing cycle is then repeated in continuing succession.

Modifications may be resorted to within the spirit and scope of the appended claims.

We claim:

1. A hydraulic motor drive indluding a main shaft, a

rotor casing encompassing said shaft and freely mounted for rotation thereon, said casing having a chamber formed therein and extending axially along said shaft, a first impeller member within said chamber and arranged for sliding contact with the inner surface areas of said casing, said impeller member keyed to said shaft and movable therewith, said casing and shaft arranged for relative rotation, a second impeller member secured to the inner surface of said casing and arranged to limit the movement of said first impeller with respect to said casing, means to restrain the movement of one of said rotative elements during rotation of the other and all of said rotative elements being movable in a single direction.

2. A hydraulic motor drive including a main shaft, a rotor casing encompassing said shaft and mounted for rotation thereon, said casing having a chamber formed therein and extending axially along said shaft, an impeller member within said chamber and arranged for sliding contact with the inner surface areas of said casing, said impeller member keyed to said shaft and movable therewith, said casing and shaft arranged for relative rotation, a second impeller member formed upon at least one portion of the inner surface of said chamber and arranged to limit the movement of said first impeller with respect to said casing, stop means to limit the amount of relative rotation of "both said rotative elements, locks arranged to restrain the movement of one of said rotative elements during said relative rotation, the rotation of all said movable elements being in the same direction, and means to supply fluid under pressure to opposite sides of said first impeller in timed sequential relationship.

3. A hydraulic motor drive including a main shaft, a rotor casing encompassing said shaft and mounted for rotation thereon, said casing formed with a chamber therein, said chamber extending axially along and around said shaft, an impeller member within said chamber and arranged for sliding contact with the inner surface of said casing, said impeller member keyed to said shaft and movable therewith, means mounting said shaft for rotation about its longitudinal axis, impeller surfaces formed upon the inner surface of said chamber and arranged to limit the movement of said impeller member with respect to said casing, hydraulically operated locks arranged to alternately restrain said casing during the relative rotation of said shaft, and to restrain said shaft during relative rotation of said casing, means to limit the amount of relative rotation of said shaft and said casing, the rotation of said shaft and casing being in one direction, and means to afiect the movements of said casing and said shaft in timed relation.

4. A hydraulic motor drive including a casing, 21 chamber formed within said casing and extending axially thereof, a shaft coaxial with and extending through said casing, a first pair of oppositely disposed radially extending vanes carried by said shaft in the zone encompassed by, said casing, said vanes arranged for lateral movement in a single direction in said chamber and to a distance less than the full circumference of said casing, a second pair of vanes mounted on said casing and extending into said chamber, means mounting said casing for rotation with respect to said shaft, said shaft and said casing being rotated relative to each other by the introduction of fluid into said chamber, a plurality of fluid passageways formed in said shaft and leading into said chamber at opposite sides of said radial vanes, means for selecting a plurality of said passageways for the entrance of fluid under pressure into said chamber, the remaining passageways acting as the fluid return from the chamber, and cam operable means for selectively passing the fluid to said passageways for controlling the sequential introduction of fluid into said chamber.

5. A hydraulic motor comprising an output shaft, a casing surrounding and extending along said shaft to form an annular chamber, a first radial vane extending the length of said chamber and adapted to rotate with said shaft, a second radial vane extending the length of said chamber and adapted to rotate with said casing, means for periodically locking said shaft against rotation, means for periodically locking said casing against rotation, said locking means being operative in succession: and means for alternately introducing fluid under pressure to said chamber on opposite sides of one of said vanes, whereby said shaft and casing are alternately locked and alternately rotated.

6. A hydraulic motor comprising an output shaft, means mounting said shaft for rotation about its longitudinal axis, a casing surrounding and extending along said shaft to form an annular chamber, said casing being rotatably mounted on said shaft, a first radial vane extending the length of said chamber and adapted to rotate with said shaft, a second radial vane extending the length of said chamber and adapted to rotate with said casing, means for periodically locking said shaft against rotation, means for periodically locking said casing against rotation, said locking means being operative in succession and means for alternately introducing fluid under pressure to said chamber on opposite sides of one of said vanes, whereby said shaft and casing are alternately locked and alternately rotated.

7. A hydraulic motor comprising an output shaft, a casing surrounding and extending along said shaft to form an annular chamber, a first radial vane extending the length of said chamber and adapted to rotate with said shaft, a second radial vane extending the length of said chamber and adapted to rotate with said casing, means for periodically locking said shaft against rotation, means for periodically locking said casing against rotation, said locking means being operative in succession, means for alternately introducing fluid under pressure to said chamber on opposite sides of one of said vanes, means for exhausting fluid from said chamber on the side of said one vane opposite to the side receiving fluid under pressure, and throttle valve means operable in said exhausting means for regulating the rate of exhaust of fluid from said chamber, whereby the rate of rotation of said shaft and casing may be selectively controlled.

8. The hydraulic motor defined in claim 7 wherein the position of said throttle valves are controlled throughout the exhaust period by cams moving in synchronism with the rotation of the shaft and easing.

9. The hydraulic motor defined in claim 7 wherein said exhaust regulating means comprises a pair of openable and closable throttle valves, one throttle valve regulating the rate of exhaust during rotation of said shaft and the other throttle valve regulating the rate of exhaust during rotation of said casing.

10. The motor of claim 7 further including a radially extending plate keyed to said shaft, said plate having a portion of its periphery cut away, a projection carried by said casing, said projection extending into the cut out portion of said plate, whereby relative rotation of said shaft and casing are limited to an angle determined by the amount of the cut away portion of the plate minus the width of said projection.

11. A hydraulic motor comprising an output shaft, a casing surrounding and extending along said shaft to form an annular chamber, a first radial vane extending the length of said chamber and adapted to rotate with said shaft, a second radial vane extending the length of said chamber and adapted to rotate with said casing, means for periodically locking said shaft against rotation,

means for periodically locking said casing against rotation, said locking means being operative in succession, means for alternately introducing fluid under pressure to said chamber on opposite sides of one of said vanes, means for exhausting fluid from said chamber on the side of said one vane opposite to the side receiving fluid under pressure, and means operable in said exhausting means for regulating the rate of exhaust of fluid from said chamber, whereby the rate of rotation of said shaft and easing may be selectively controlled.

12. A hydraulic motor comprising an output shaft, a casing surrounding and extending along said shaft to :form an annular chamber, a first radial vane extending the length of said chamber and adapted to be rotated with said shaft, a second radial vane extending the length of said chamber and adapted to rotate with said casing, means for periodically locking said shaft against rotation, means for periodically locking said casing against rotation, said locking means being operative in succession, means for alternately introducing fluid under pressure to :said chamber on opposite sides of one of said vanes, means for exhausting fluid from said chamber on the side of the vane opposite to the side receiving fluid under pressure, and throttle valve means operable in said ex- Ihaust means for regulating the rate of exhaust of fluid from said chambers, whereby the rate of rotation of said shaft and easing may be selectively controlled.

13. A hydraulic motor comprising an output shaft, means mounting said shaft for rotation about its longitudinal axis, a casing surrounding and extending along said shaft to form an annular chamber, said casing being rotatably mounted on said shaft for rotation, a first radial vane extending the length of said chamber and adapted to rotate with said shaft, a second radial vane extending the length of said chamber and adapted to rotate with said casing, means for periodically locking said shaft against rotation, means for periodically locking said casing against rotation, said locking means being operative in succession and means for alternately introducing fluid under pressure to said chamber on opposite sides of one of said vanes, whereby said shaft and casing are alternately locked and alternately rotated.

14. A hydraulic motor comprising an output shaft, means mounting said shaft for rotation about its longitudinal axis, a casing surrounding and extending along said shaft to form an annular chamber, said casing being rotatably mounted on said shaft for rotation, a first radial vane extending the length of said chamber and adapted to rotate with said shaft, a second radial vane extending the length of said chamber and adapted to rotate with said casing, means for periodically locking said shaft against rotation, means for periodically locking said casing against rotation, said locking means being operative in succession and means for alternately introducing fluid under pressure to said chamber on opposite sides of one of said vanes, whereby said shaft and easing are alternately locked and alternately rotated.

References Cited in the file of this patent UNITED STATES PATENTS 530,220 Delattre et al Dec. 4, 1894 1,117,516 Petrie Nov. 17, 1914 1,130,920 Miller Mar. 9, 1915 2,512,731 Adams June 27, 1950 2,701,448 Johnson Feb. 8, 1955 2,924,199 Lawson et a1. Feb. 9, 1960 

